Change speed transmission for machine tools



March 2, 1954 H. SCHOEPE ETAL 2,670,633

CHANGE SPEED TRANSMISSION FOR MACHINE TOOLS Filed Dec. 7, 1951 5Sheets-Sheet l JNVENTORS l-m/eey SCHOEPE HENRY 144 SPFE/TZEE ,qrromve sMarch 2, 1954 SCHQEPE ET AL 2,670,633

CHANGE SPEED TRANSMISSION FOR MACHINE TOOLS Filed Dec. 7, 1951 5Sheets-Sheet 2 LVVENTDRS HHPEJ'SCHO%E' BY HENRI w JPBlE/TZEE March 2,1954 H- SCHOEPE ETAL CHANGE SPEED TRANSMISSION FOR MACHINE TOOLS 5SheetsSheet 3 Filed Dec. '7, 1951 INVENTORS H/IPE') .SCHOEPE /ENP) IMSPEE/TZfE March 2, 1954 H. SCHOEPE ET AL CHANGE SPEED TRANSMISSION FORMACHINE TOOLS Filed Dec. '7, 1951 F/L TEE 5 Sheets-Sheet 4 JUMP I L g fI ,qTTZZi fY S INVENTORS HAPPY SCf/OEPE N Y HE/VE) w. ve /r252 O y B K71 March 2, 1954 H. scHOEPE ErAL 2,670,633 CHANGE SPEED TRANSMISSION FORMACHINE TOOLS Filed Dec. 7, 1951 5 Sheets-Sheet 5 I IN V EN TORS HARE0405/25 By HEMP) 5, 557% Patented Mar. 2, 1954 CHANGE SPEED TRANSMISSIONFOR MACHINE TOOLS Harry Schoepe, Seven Hills, and Henry W. Spreitzer,Parma, Ohio, assignors to The Warner & Swasey Company, Cleveland, Ohio,a corporation of Ohio Application December 7, 1951, Serial No. 260,408

18 Claims. (01. 74-359) This invention relates to a change speedtransmission particularly adapted to be used in the headstock of amachine tool and the contro1 for said transmission.

In modern machine tools it is desirable that the rotating work or toolspindle be capable of being driven at a relatively large number ofdifferent speeds. In order to provide the desired large number ofdifierent speeds of the spindle the change speed transmission in theheadstock tends to be bulky, to require the use of long shafts and tonecessitate unduly large headstocks. This is especially true withrespect to smaller size machine tools, such as small size turret lathesand the like.

An object of the present invention is to provide an improved and novelchange speed transmission in the headstock of a machine tool whichcapable of imparting a relatively large number of different speeds tothe spindle but at the-same time is compact, utilizes-relatively shortshafts and enables the overall size of the headstock to be kept at aminimum.

It is desirable in machine tools that the change speed transmission inthe headstock be silent in operation and such that the speeds can bechanged under load easily and without danger of damaging the parts, anda further object of the present invention is to provide a change speedtransmission for the headstock of a machine tool which accomplishes theadvantages referred to.

-A'further object of the invention is to provide a'change speedtransmission in the headstock of a machine tool which is so constructedthat certain of the engageable and disengageable elements of thetransmission may be simultaneously engaged to produce a braking actionon the spindle and without likelihood of damage to the parts and withthe further advantage that special brake mechanism for the purpose ofbraking the spindle is eliminated and the function of such special brakemechanism is obtained through a predetermined operation of the changespeed elements of the transmission.

A further object of the invention is to provide in a transmission for aheadstock of a machine tool such as referred to in the preceding objectsimproved means for effecting the speed changes quietly and while underload and for effecting the braking of the spindle, together withimproved controls for said means.

A still further object is to provide in a transmission for a headstockof a machine tool such a referred to in the preceding objects improvedcontrol means for the transmission such that during spindle rotation ata certain speed in one operative step of the work cycle a differentspindle speed can be preselected for the next operative step and thenreadily obtained at the end of said one operative step.

An additional object is to provide in a transmission such as referred toin the last named object improved control means such that movement ofsaid means in one direction effects preselection of the spindle speedsand movement thereof in another direction obtains the preselected speed.

Further and additional objects and advantages not hereinbefore referredto will become apparent hereinafter during the detailed description of apreferred embodiment of the invention which is to follow and whichembodiment is illustrated in the accompanying drawings, wherein Fig. 1is a fragmentary front elevational view of a machine tool showing theheadstock thereof and wherein is used a change speed transmissionembodying the invention.

Fig. 2 is an end elevational view of the headstock of the machine toolshown in Fig. 1 and is taken looking from the left hand side of Fig. 1from a position substantially indicated by line 2 --2 of Fig. 1. Fig. 3is a developed partial sectional and partial elevational view of aportion of the change speed transmission in the headstock and embodyingthe present invention, said portion including that part of thetransmission formed by the input shaft, the forward and reverse shafts,one of the change speed gear shafts and the corresponding clutches.

fig. 4 is a view similar to Fig. 3 and showing the remainder of thechange speed transmission and including the spindle in the headstock.

Fig. 5 is a diagrammatic view of the change speed transmission shown inFigs. 3 and 4 and of the hydraulic control and operating circuits forthe transmission and which include the main control valve and the speedselector valve.

Fig. 6 is a longitudinal section of the main control valve in theneutral position.

Figs. 7 to 10 inclusive are transverse sectional views taken,respectively, on lines 'l-l, 8--8, 9-9 and |0l0 of Fig. 6.

Fig. 11 is a longitudinal section of the speed selector valve, and

Figs. 12 and 13 are detail views of certain parts of the speed selectorvalve which are duplicated a number of times in the speed selectorvalve.

Referring to Fig. 1, the bed of the machine tool is indicated at H andat one end of the bed is the headstock l2. The bed is provided withparallel front and rear ways l3 which extend from the headstock towardthe other end of the bed and upon which ways the slides of the machinetool move toward and from the rotatable work spindle mounted in theheadstock 12 on an axis parallel to said ways as is well understood inthe art.

Further description of the general features of the machine tool need notbe explained in detail since they are well understood in the art. I

The source of power for the change speed transmission in the headstockand'which transmission and its control means embody the presentinvention may be any suitable source .of power. For purposes ofillustration the source of power is indicated as an electric motor 14supported by the bed adjacent the end thereof which is provided with theheadstockand said motor I l may drive a'p'ull'ey 15 mounted on a powerinput shaft it, said'drive to the pulley being by way of a suitablepulley on the shaft of the motor l4 and a belt extending between saidsuitable pulley and the pulley l5 as will be well understood in the art.

The power input shaft l6 extends into the'headstock-through the end wallthereof and is rotatably supported suitable bearings formed in sald'endwall, as clearly indicated in Fig. 3, and has fixed to it within theheadstock and adjacent to said end wall a drive gear ii. The drive gearll meshes with agear i8 that is formed on a clutch sleeve lil whic'h isfreely rotatable on an elongated sleeve 23 which is keyed to a reverseshaft 2! extendin parallel to the power input shaft is and supported insuitable bearings "formed in the headstock. The gear :8 and the clutchsleeve 19 are held against axial movement in one direction relative tothe elongated sleeve 26 bya shoulder formed on the latter and in theother'direction by the head-of a headed sleeve'22 which is fixed in aninternal supporting'portion of the headstockand within which sleeve 22the reverse shaft 2| rotates. The reverse shaft '2! is-maintainedagainst axial 'displacement relative to'the sleeves 20 and22 by a-collar'23 secured to one end of the shaft 2| and engaging the end of thesleeve '22 and by'a reverse-gear '26 fixed to the shaft 2! and engagingthe adjacent end of the elongated sleeve 29 andals'o bya-collar 25 fixedto the end'of the shaft2i and-engagingthe bear ing in the headstockwhich supports the last mentioned'end of the shaft.

The clutch sleeve lt'whlch has formed thereon the gear i8 mountsinternally spaced clutch plates 25 and said clutch plates 28 alternatewith clutch-"disks 21 which are fixed to the elongated sleevelt torotate therewith. The clutch provided by the plates 26 and disks 2'! isof the friction type so that slippage may occur when 'apredete'rminedload-has been exceeded.

The-elongated sleeve 28 has integral therewith or fixed thereon acup-shaped housing 28, the open end of which is adjacent to the clutchin the sleeve 19 and said-'housing slidably mounts a piston-like clutchactuator 29 which engages the end clutch disk '21, whereforeif the"actuator29 is moved toward the-clutch in the sleeve is the disks 2-!and clutch plates 26 will be pressed into frictional driving contactwith each other to .cause the clutch sleeve 19 and gear Il'8 to impartrotation-to the elongated sleeve 20 'and thereverse shaft 2-! as will bewell understood in the art-.-

The clutch actuator 29 is provided with one or more spring plungers 38which engage the end clutch disk 21 and function to move the clutchactuator inwardly of its housing 28 to engage the bottom wall of thehousing and to effect driving disengagement of the clutch plates 26 andclutch disks 21.

The clutch actuator 29 is moved in the clutch engaging direction byfluid pressure power such as hydraulic pressure. It will be understoodthat the clutch actuator might be moved by other power means, such aselectrical or mechanical, if desired, and misunderstanding applies tothe actuators of other clutches later to be described. The pressuremedium is brought into the housing 28 to act on the actuator 29 andeffect engagement of the clutch in the clutch sleeve i9, such clutchbeing hereinafter designated as the reverse clutch, by means of a bore31 in the sleeve 20 which communicates at all times with a radial port32 formed in the shaft 2|, it being recalled that said shaft and theelongated sleeve '28 are keyed together for rotation as a unit.

The port 32 communicates with one end of an elongated axial bore 33formed in the shaft 2|. The opposite end of the bore 33 communicates byway of a radial port with an annular groove '34 formed in thecircumference of the shaft 21 and said groove 34 communicates at alltimes through one or more ports with an annular groove 35 formed in thecircumference of the fixed sleeve 22. A supporting block or bushing 36surrounds the sleeve 22 :and is fixed in a portion of the headstockwall. The block or bushing 35 is provided in its outer circumferencewith an annular groove 3! that is in communicationwith the annulargroove 35 of the sleeve 22 by means of a port-.38. The block or bushing36 preferably is provided on its outer circumference on opposite sidesof the groove '3'! with sealing grooves in which aremounted suitablesealing means, such aswell known '.0-rings. The annular groove 31 in theblock 36 communicates with a bore '39 formed .in the interior wall ofthe headstock and mountin therein a threaded-coupling fitting 4% .power:input shaft IB and the reverse shaft 2|.

.-A gear is fixed to the elongated sleeve 43 and meshes with the gearl lfixed to the reverse shaft 24. It will be noted that when the reverseclutch on the reverse shaft 2| is engaged then the'elongated sleeve 43and the forward shaft M .will berotated in the same direction to therotation of the input shaft 16 through the gears ll, 18, 2d -and45,provided the forwardclutch on the shaft Misdisengaged.

A cup-shaped housing 46 integral with the sleeve 43 and similar to thehousing 28 of the sleeve :28 contains the actuator for theclutch intheiforward clutch sleeve 42. 'Itwill be understood that the clutchplates and disks in the forward clutch within the sleeve 42 and'theactuator within the housing 46 are the same in construction as thecorresponding parts of the l'evereclutc'h onthe-sleeve 20. p

It will further be understood that when the forward clutch is --engagedthe -shaft '44 and sleeve 43 will be rotated in the opposite directionto the rotation of the power input shaft l6, the

drive including the gear I1 and the gear 41.

A clutch sleeve 41 is freely rotatable on the elongated shaft 44 and isdesignated a high clutch sleeve and has formed thereon a gear 48, itbeing understood that said clutch sleeve 41 and gear 48 are held againstaxial movement relative to the elongated sleeve 43 by any suitable anddesirable means.

A housing 49 for the actuator of the clutch in the sleeve 41 is integralwith the elongated sleeve 43 and corresponds to the housings 28'and 46previously described. It will also be understood that the clutch platesand disks in the sleeve 41 are similar in construction to thecorresponding parts in the previously described clutches.

It will be seen that when the high'clutch on the sleeve 43 is engagedthen the gear 48 will rotate with the sleeve 43 and shaft 44, it beingrecalled that said sleeve 43 and shaft 44 will rotate in a forwarddirection and opposite to the rotation of the shaft [6 when the forwardclutch is engaged and the reverse clutch on the shaft 2| is disengaged.

It will also be recalled that when the forward clutch is disengaged andthe reverse clutch is engaged then the sleeve 43 and shaft 44 will bedriven from the shaft 21 through the gears 24 and 45 in the reversedirection which is the same direction as the rotation of the input shaftl6.

The left hand end of the shaft 44 as viewed in Fig. 3 extends into asleeve 59 similar to the previously described sleeve 22, while the righthand 4 end of the shaft 44, as viewed in Fig. 3, is rotatably supportedin a bearing formed in the headstock and is held against axial movementby suitable means such as the retaining collar and shoulder indicated.

In order to actuate the clutch actuators i and 52 in the housings 46 and49, respectively,

the following provision is made forbringing fluid pressure to theactuators. The shaft 44 is provided with an axial bore 53 which extendsfrom adjacent the left hand end of the shaft as viewed in Fig. 3 toadjacent the gear 45.

Centrally mounted in the axial bore 53 is a tube 54 which is supportedin the bore by supporting plugs so as to have between said plugs anannular chamber surrounding the tube 54. The shaft 44' to the left ofthe left hand plug in Fig. 3 is'provided on its circumference with anannular groove 55 which communicates with the bore 53 conduit of thehydraulic circuit is connected as will later be referred to. It will beseen that fluid pressure in said conduit will flow through the passage60, grooves 58, 56 and 55 into the bore 53 of the shaft 44 and thencethrough the tube 54 until it has passed the right hand plug as viewed inFig. 3, from whence it flows through the bore 53 and into a passage 6!that extends into the housing 49 of the high clutch actuator. The shaft44 is provided on its circumference to the right of the left handplug,as viewed in Fig. 3, with an annular groove 62 that communicates bymeans of a port with the annular space surrounding the tube 54.

The groove 62 communicates by means of a port with an annular groove 63formed in the circumference of the sleeve 50 and said latter groovecommunicates by means of a passage 64 with an annular groove 65 in thecircumference of the block or bushing 59. The groove 65 come municateswith a passage 66 in the headstock wall which is connected to a conduitof the hydraulic circuit later to be referred to. The annular space inthe shaft 44 surrounding the tube 54 communicates with a port 6? in theshaft and said port in turn communicates with a passage 69 in the sleeve43 and leading to the actuator in the housing 46 for the forward clutch,wherefore it will be seen that fluid pressure can be introduced to thehousing to move said actuator to effect engagement of the forwardclutch.

Fixed to the sleeve 43 and shaft 44 to the left of the gear 4|, asviewed in Fig. 3, is a gear 69 While a gear 16 is fixed to the sleeve 43and shaft 44 to the right of the gear 45. The gear 69 meshes with alarger gear H formed on a low clutch sleeve 72 that is freely rotatableon an elongated sleeve 13 keyed to shaft 14. Thegear 48 meshes with agear E5 formed on a housing 16 for a clutch actuator later to be.referred to and which housing is integral with the elongated sleeve 13and consequently rotates with said sleeve and shaft 74. The gear 16meshes with a gearrll formed on a clutch sleeve 16 that is freelyrotatable on the elongated sleeve 13. v p I It will be seen that byselectively engaging the clutches in the sleeves Hand '78; the elongatedsleeve 78 and the shaft 14 can be driven through the gears 99, H, 48, i5and i9, it at any one of three speeds relative to the shaft 44. It willbe understood that the clutch plates and the clutch disks in the clutchsleeves l2, l6 which may be designated, respectively as a low clutch anda medium clutch are the same in structure as in the previously describedclutches.

In addition to the housing l6 for the actuator of the clutch in thesleeve '58, the elongated sleeve 13 is provided with an actuator housing79 for actuating the clutch in the sleeve '52. It will be understoodthat the'actuators in the housings l6 and 79, indicated respectively atB9 and 81 are similar in construction to the actuators of the previouslydescribed clutches.

The left hand end of the shaft Z4 as viewed in Fig. 3 extends into asleeve 82 mounted in the wall of the headstock and similar to thesleeves 56 and 22 already described. It will also be understood that theshaft '54 and elongated sleeve 13 are maintained against axialdisplacement. The shaft 14 is provided with an axial bore 83 in which iscentrally mounted an axially extending tube 84 similar to the previouslydescribed tube 54 and supported in the bore 33 by blocks mounted thereinadjacent the opposite ends of the tube. v

It will also be seen that intermediate the blocks there is an annularspace surrounding the tube 8 and said annular space communicates bymeans of a radial passage in the shaft and a passage 86 in the elongatedsleeve 73 with the interior of thehousing F9 for the actuator 8|, itbeing noted that said passage is located just to the left of the righthand plug for the tube 84 as shown in Fig. 3. a

The extended end of the bore 83 to the right of the right hand end ofthe tube 84 (as viewed in Fig. 3) communicates with a radial passage 7 6in the shaft 3 which t rns c nmumqates with a passage 8! in the sleev e13 and leadiifl 5P0 .the interiorof the housing ,16 for theclutclractuator flfl.

-.The shaft-1141s prov ded w t a imuin ersn ia roove .88 adjacen it lftihand and i t .r communicates with the 11 91 183 i y of port located17042116 left as view d li ies-1 o the -left hand bl c tha shon -rte t etul e the The circumferential :g ZQQ fi e 3 c mmuni a es .4 3 may of amart with vaqcircumferential ,grooye 3 8 stormed tin-the ;,s.1e e 582-..a d s id. oo e comlmunicates by means of a passage 8.5 with acircumferential em t s91 imm s n a ti supheltii block orrbushinfliisimilar:tothezhloqk i fi ils .ings 59 and 36 previously {describedThegrooYe '91 .islconnected to a conduit of the hydraulic circuit :latervto be referred to. -{I he -shafti14 to the right ofthesleft-hand-blockwhich supports the tube :84 ais provided With-acircumferential groove 33 that. communicates with the annular spacehetweent'thektubevaa and;the=;wall of the bore 63 inthe shaftllbyemeans-of alsuitable port. The circumferential groovetflsom-"municates by means of a port with; a. circumferential groove M; formedinzthe sleet/e332 andsaid .groove 94 communioates'in turnwith a passage95 in the block. or'bushing .92 and extending ,to a circumferentialgroove 9B1which in turn-is connected 'to a conduitof the hydrauliccircuit as will later be explained.

It will be seen that hydraulic-pressure can be introduced to the-tube 84through thegroovevsi, passage 90 and grooves 39, 88 to actuate theclutch-actuator 80 in'the housing it to engage the clutch members in thesleevei'lfl, so that the gear 7] will be clutched to-theelongated sleeveis and shaft 14. Likewise it will be-seen that hy- ,draulic pressurecan'be introduced to the bore I83 throu h the groove dfipassage'fi-andgrooves .53 and Sdtoactuate the clutchact-uator-Bl in thehousing 19 to engagethe clutch elements in thesleeve-n to clutch the,gear'H to the elonigatedgsleeve l3 and the shaftfbi.

A;gear 9? ,is fixed to the elongated sleeve 13 and shaft M intermediatethemgear 1| and the sleeve-82. Also agearfii? is fixed to theshaitM :andelongated sleeve J3 adjacent-to the right hand end of the shaft asviewed i11 Fig. -.3.

The gear 91 -meshes-with a larger gear .99 formed on a clutch sleeve 360which isfreely rotatable on an elongated sleeve It! thatiskeyed to ashaft I62 parallel to the shafts id itii and I6 and rotatablysupportedin the-headstock I in suitable bearings.

It will be understood that containedlin the clutch sleeve I69 aresuitableclutch plates, and disks-similar to the corresponding elementsin the clutches previously described. The elongated sleeve H .isprovided with an integral :cup-shaped housing 103 Which-contains thereina piston-like clutch actuator 184 for .e fecting engagemento-f theclutch elements in the sleeve I00. It will be noted that the sleeve it!).is provvided with a circumferential recess .to accom-- modate the gear'il previously described.

The gear 98 on the shaft M constantly meshes with a gear I65 formed-onaclutch sleeve lei: that is freely rotatable on the elongated sleeve mland contains clutch plates and'dishs similar to the elements in thepreviously ;;described clutches.

The elongated sleeve l6 I is provided with an Q Q ctuat v .0.8 o en a nth element o clu ch n t e t r -U t egq ctt res a 95 to the elongatedsleeve Hand ;to.the shaft lQZ.

'When theidrive to the shaft 102 is through the gear 99 it will be at areduced rate coinpared to the shaft 1A and when it is through the gearI95 it will be at an increased rate. It l al ofb see h th ha t W a h zdrn a m on -In s e s as ompar d to th forward shaft 44 and the reverselshaft 2.l [depending upon the selective engagement ,of ,the clutchesonthe shafts 44,-1.4 and 102, as already described.

The shaft 502 is provided with an axial .bore {09 in which a tube it iscentrall y supported by means .of circular blocks amounted adjacent theopposite .ends of the tube MD. A radial .port lll in the shaft 102communicates with.-'the annularspace between the wall ofthebore {9.9and-,tl' e tube H8 andtwith apassage1.12 formed in the elongated sleeveJill and communicating with the interior of the actuator housing U13 andwith the clutchractuator 1M. An elor'igated radial port 1 53 in the"shaft J02 communicates with the bore 109 to the right ofithe right handvend of the tube .0 and hence with said tube and @also with a passage M4in the elongated l v "H and wh P s ex en s a th ac ua o tin th ihe e nl- The deft hand ,end .of the shaft J92 extends into asleeve l l 5similar to the SIeeves S Z SiLand 22 previously described. The shaft I02is provided with a circumferential groove ,l lB gthat communicates withthebore it}! to the left of the left hand circular block that '.supportsthe .tube lit-as viewed.in;Fig. a. The gro ove M5, .in turn,communicates by way pf a port .in the sleeve H5 --with a circumferential'Qgroove H] gformed in the-sleeve (H5. The. circumferential groove H'lcommunicates throug h a passagelifi with a circumferentialgroove7lL9formed in a supporting block or bushing. I similar to the I blocks :orbushings 59 2, viii] and previously 518- -s.crib d- I ,Theannular groovei [i communicates with .a m sa 1: ti m z n h :h e w an so nected to aconduitof-the hydraulic circuitdater to be refcrred to. It will be seenthat; hydraulic pr ssur i :th ss 1- l fl w i m h th groove il-sgpassagel tfi grpovesfl i1 andll ltir to :the bore |;&9;i n theshaftr I m-land thence through .the tube l I 9 to the extreme -righthand enipf the ;bore H39; from whence; it passes through the port i lfsand passage 1 it v to the interiorl of .ithe 'hous nsslfi 1 t e tuet ihpa tu t t ifl-t cneaee 7 the clutch elements; in the clutch sleeve 1013'and elutch the gear -to the-.elongated sleeve ml -an tt -th hef W Theshaft M32 is provided .with acircumier- :entiahgrooveAZZ thatcommunicates hyewayof la port with-the; annular :space hetween theftub een ath M13 o i 'hebe 'z n h hefisuch: communication" occurrlng to theright ,of the as han c in s p rtin 1 f h "tub H0.

QQI'L-Q Y it communicate b e p ili isz rcumf en e te 3 1, QPmfi .inrthsle v iwn t a ea v 4.2a t m cmr tm s e t r ssa fi e nd n tt 5.2.circumferential groove ,1 25, formedainfithe supmo t se hos e -mosh n2,0- Th m r $.2 esomme i e e w thf see a fi r e ii rlh heaglstock walland to whichwpassageis g nsmotee c du p ;the' vdr uli imuite m integralcup-shaped housing 101 {containing an-g5riaterbe reigrred to. r

- sleeve It will be seen that, hydraulic pressure in the passage I23 isintroduced to the annular space I sage I 23, and grooves I23 and I22.The hydraulic pressure thus introduced to the annular space referred towill fiow through theradial port I II and passage LIZ into the housingI03 to actuate the actuator I04 and engage the clutch elements in theclutch sleeve I69 to clutch the gear 99 to the elongated sleeve Ill! andto the shaft I02. The shaft I02 and elongated sleeve IOI has fixedthereto intermediate the gear 99 and the sleeve H5 a gear I27 whichmeshes with a gear I fixed to an elongated sleeve I29 that is keyed to ashaft I30 rotatably supported in suitable bearings in the headstock asare the previously described shafts and extending parallel to saidpreviously described shafts.

It will be seen that the elongated sleeve I29 and shaft I30 are alwaysdriven from the shaft I02. through thegears I2'I, I28 at any one of .sixdifferent speeds. A clutch sleeve I3I is freely rotatable on theelongated sleeve I 23 and contains clutch plates and disks similar tothe corresponding elements .in the previously described clutches.

The sleeve I3I has formed thereon'a gear I32 which thus can be clutchedto the elongated sleeve I23 and shaft I30 or declutched therefrom. Thesleeve I29 has formed thereon a cup-shaped housing I33similar'to theclutch actuator housings previously described and which-contains theactuator I34 for the clutch elements in the clutch sleeve I3I. Theelongatedsleeve. I29 to the right of thehousing I33, as viewediin Fig.4, is provided the shaft I30 and which port in turn communicates with apassage I38 that extends into the housing, I33 and functions to supplyhydraulic pressure to the actuator I34. I

The left hand end of the shaft I30 extends into a sleeve 139 similar tothe sleevesIIS, 82,

-50 and 22 previously described. The left'hand end of the shaft I30 isprovided with a circumferential groove I40 that communicates by way of aport with theleft hand end of theiaxial bore :30 that is formed in theshaft. The groove I40 in-turn communicates through a port in the I33with a circumferential groove I4I formed in said sleeve and the latteris always in communication with a passage I42 formed in a su portingblockor bushing I43 that issim'ilar the clutch elements in theclutchsleeve I3I and thus to connect the gear I32 to the elongatedsleeve I29 and. the shaft I30.

The gear I32 constantly meshes with a smaller gear-"I45 fixed to thework or'tool spindle I43 that is 'rotatably mounted insuitable'bearings-in the headstock and which is parrallel to the shaftsI30, I02, I4, 44 and 2I. It will be seen that when the gear I32 isclutched to the elongated sleeve I23 and shaft I30 that then the spindleI46 will be driven at an increased rate through the larger gear I32 andthe smaller gear I45. The gear I35 fixed to the elongatedsleeve I29 andshaft I30 constantly meshes with a larger gear I41 formed on a clutchsleeve I39 that is freely rotatable onthe spindle I46 and which containsclutch plates and disks similar to the corresponding elements in thepreviously described clutches and with the clutch disks thereof fixed tothe spindle I46.

A housing I49 for the actuator I50 that engages the clutch elements, inthe clutch sleeve I48 is carried by the wall of the headstock and isprovided with an opening within which the spindle I46 rotates, saidhousing extending into the sleeve I40 within that portion upon which thegear I41 is formed and to the right of the clutch elements in the clutchsleeve I48.

The housing I49 is provided with a continuous passage I5I extending tothe clutch actuator :I59 and communicating with aijpassage I52 formed inpart in the housing I49 and in part in a collar I53 fixed on acylindrical portion of the housing and within which portion thespindle'I4B rotates.

A conduit of the hydraulic circuit as later will be explained isconnected to the end of the passage I52 in the collar I53 and it will beseen that hydraulic pressure can flow from the conduit through thepassages I52, I5I to the clutch actuator I50 to engage the clutchelements in the clutch sleeve I48 and thus drive the spindle I49 fromthegear I35 through. the gear M1 at a reduced rate.

From the foregoing description it will be evident thatthe spindle I40can be driven at any one of twelve different speeds from the forwardshaft 44 or at any one of twelve different speeds from the reverse shaft2|, depending upon the selective'engagement of the clutches hereindescribed.

It will be noted that the arrangement of the shafts, clutches andgearing is such that the change speed transmission is compact and can becontained in a headstock of relatively small size notwithstanding thefact that the transmission provides for imparting to the work spindle'alcomparativelylarge number of different speeds.

- As will be later pointed out, certain of the draulically.

clutches'in the transmission can be simultaneously engaged to provide abraking arrangement for the rotating spindle and such arrangementrequires no additional brake mechanism and is perfectly safe in-that theclutches being friction clutches providethe necessary slippage in caseof overload. Also it will later be pointed out that by simultaneouslydisengaging certain of the clutches in the transmission and particularlythe clutches in the clutch sleeves I3I and I48 a neu- .-tral arrangementof the transmission can be selected and one wherein the spindle I43 is afree spindle as is often desired in the operation of a machine tool.

ated actuators and control mechanisms for selecting or preselecting thespindle speeds, although for purposes of illustration the clutches havebeen shown as actuated and controlled hybiomass l 1 Referring toFig. 5',a hydraulic circuit is'scheinati'cally illustrated and includes a pumpF54 connected by conduit- Iii-with a sump I562 The pumpm'ay' be drivenfrom the main drive motor It or from: an independent drive source aswill bewell understoodl The output side of the pump is connected to aconduit I51 which, in turn, is

connected by" a branch conduit lfi'l'a to the central; bore or'passagein the rotatable valve body-of a. maincontrol' valve indicatedgenerallyat C and later tobe' described in greater detail.

Thepressureline conduit I'5'I'may'also be connected by a short branchpressure line I'5I-b toa pressure gauge I58. The mainpressureline'conduit I55 extends toaspeed selector or preselector valveindicated generally at S and containing a plurality of: shiftabletwo-position valves with two of said two-position valves being connectedwith the main pressure line- I51 by branches w th and: k514i;

The. rotatable valve body of the main control valve C which; is mountedon. the front'of the headstock is: provided with a; forwardly extending"shaft portion i591, to the: outer end: of

which; is connected an. operating lever Hi0, see

Figs. 1i and; 6, conveniently located on; the front of the headstocls.llhe speed selector-or preselec tor valve: S; is controlled and actuatedthrough the medium of a, shaft I6I which is rotatablev to selectorprescient the spindle speeds: and is axially shiftabletoohtaintheselected oirp-reselected speeds and; extends into the housing; of; thespeed selector or'preselectorvalveiand isprovidecton' its outer end;with. an operating wheel Ol'.'k1IGb: Hi2,

see 1,. 5 and; 11-, its-being noted that the speed selector; or'preselector' valve iS-In'OLllIi'fied; on the: top of. the headstockanclalso: that: the hand wheel or knob I62 is within easy reach. itheorierator from; hispositiorr in frontof the machine as is also thelever Izfiil of theimain; control valve.

'Ihefitting 40' that. isscrewed into the passage 39: is connected: to a:conduit I63? that extends to:- and is operatively' connected with themain control valve; wheretore when said: main control valve is properlypositioned hydraulic pressure can. be introduced; to: the: boreid in:the reverse shaft 2.1 to actuate the clutch actuator 2d and engage: theclutch elements. in the: reverse clutch: sleeve I9 to clutch said;sleeve: and the gear I 8 to the: elongated sleeve lit and; the re.-

verse shaft 2i; A: conduit. Hi4: is connectedtto the passage, 66* andextends to: the control valve C, wherefore hydraulic pressure can becaused: to. act on the actuator St for the clutch elements in theforward clutch: sleeve 4'2 1to connect saidsleeve and the gear 4I- withforward shaft 44.

A- conduit Hi5 extends between the main control. valve. C and-the. speedselector orrpreselector valve.- S and,- aswill later he explained,functions when themain control valve: is in. neutral positionto efiectsimultaneous disengagement; of. the high clutch; on'zthe' shaft Iltwhich is associated withv the gear I32. and the low clutch on thespindle I46 which is associated with the gear I41; thus-providing forafree. spindle. Atthis time certain of the other clutches hr thetransmission willbe disengaged and certain thereof engaged as will;later become apparent.

the

A conduit I66: extends: from the main control valve C. to the: speed:selector or preselector valve 8- so that when the main control. valve isinthe brake position. simultaneous engagement of any tworofthe-high, lowand "medium clutches on the shafts 44 and I4 can take place tosimultaneously operatively connect any two of the gears 43 It and H withthe respective shafts 44 and; I4, it being noted that such simultaneousconnection of the gears with their shafts will act in opposition and asa brake due to the different gear ratios and since either the gear 92!-or the gear I05 on theshaft IUZ will be connected m its: shaft as willalso either the gear 3 2 on shaft I38 or gear I 4-1 on the: spindle I45,a braking" action to the rotation of the spindle will be providedwithout necessitating any separate braking mechanism.

The main control valve C has its drainport connected by' a conduit IS?!with: the sump while the drain. ports oi the speed selector orpreselector valve are connected to sump by' a con duit I68. The passage60 is: connected with a conduit 1891 that. extends to the speed selectoror" preselector valve and: since: said passage 6!! is incommunication.withthezactuator 52 forthe high clutch elements in the:sleeve- 47 orrthe shaft t4 said high clutch. can be engaged ordisengaged hydraulically to operatively' connect ordisconnect' thegear-'48 with the forward: shaft .41

A conduit I10; interconnectstheazrmular'g'roove 98. with the speedselector or preselector: valve and hence hydraulic operation of theactuator S'Ii': forg-the clutch. elements in the low clutch sleeve T2 onshaft M can be: enacted" to control the: connection and: disconnection.of the gear H with respect. to said shaft.

Aconduit IJI interconnects thcxannularrgroove or with; the speedselector or preselector valve, wherefore the actuator 811: for the;clutch elements inv the sleeve 18- can. be controlled. toBfiEClT'COIlinec iomanc'r disconnection of the medium gear I withrespect tothe. 1:4;

A. conduit I12 interconnects: the: passage; I126 with the speedselector" or preselector' valve 5, wherefore the actuator I04 f'ortheclutch elements in the sleeve l'flll can be: actuated and controlledhvdraulically toeflectcomiectiorr and disconnectioirof the low' gear 99with respect'to the shaft: I82;

A. conduit I::1:3 interconnects the passage: I Z I with the speedselector or: preselector valve S, wherefore the: actuator I08 for theclutch element's in the sleeve H16" can be operated and controlled tosheet connectionand disconnection of the high: gear I relative to. the"'shaft I02.

A conduit I14 interconnects theannular groove I244; with the speedselector ortpreselecto'r valves, wherefore the actuator I34 for theclutch: element's'in theclutch sleeve I311 can be.hydraulically'operated' and controlled to effect: connection and:disconnection of the high gear I32 relative to the shaft I30;

A conduit I15 interconnectsthe passages- I 52 with the speed selector orpreselector valve S, wherefore the actuator I for the clutch elements:in the clutch sleeve I58 can be operated andcontrolled hydraulically toeffect connection and. disconnection of the low gear I41 with respect tothe spindle I46;

A detailed description of the main control valve C willnow' begi'ven,with particular reference to Figs. 6 to lOinclusive, wherein thevalveis'ill'ustrated in the position taken when its operating lever I50 isset in the'neutral position.

The main control valve comprises a housins H6. secured in. an opening inthe front: of the headstock and having therein a valve chamber imwhichrotatably' fits: the valve body I111 that is integral. with; orconnected to the: outwardly ex tending shaft I59. to; which theoperating: handle I is connected.

The valve casing or housing I16 is provided with a passage I18 thatcommunicates with the valve chamber and to which passage the drainconduit I61 is connected, see Figs. 6 and 7. The valve housing or casingI 16 is provided with three passages I19, I80 and NH communicating withthe valve chamber and connected, respectively, with the conduits I63,I64 and I66 which extends to the reverse clutch on the shaft 2|, theforward clutch on the shaft 44 and to the speed selector or preselectorvalve S- for establishing the brake circuit.

The valve housing or casing I16 is provided with a passage I82communicating with the valve chamber and connected to the conduit I65which extends to the speed selector or preselector valve S and functionsin the neutral position of the main control valve for obtaining the freespindle (see Fig. 9). The valve housing or casing I16 is provided with apassage I83 communicating with the valve chamber and connected to thebranch pressure supply line I 51a, see Figs. 6 and 10.

The valve body I11 is provided with a circumferential groove I84 whichis always in communication with the passage I83 and the branch pressuresupply line I51a, see Fig. 10. The valve body I11 has a diametricallyextending passage I85 communicating at its opposite ends with the grooveI84 and at its midpoint with a centrally located bore I86 that extendsaxially of the valve body toward the front of the headstock.

The valve body I11 in the transverse plane thereof indicated in Fig. 9is provided with a diametrically extending passage I81 whichcommunicates intermediate its ends with the axial bore I86 while itsopposite ends terminate in enlarged recessed or scalloped portions I88formed in the circumference of the valve body. The valve body in thisplane also is provided with a diametrically extending passage I89displaced a predetermined angle with respect to the passage I81.

In the transverse plane of the valve body shown in Fig. 8 said body isprovided with a diametral passage I89 which communicates with the axialbore I86. Also the valve body in this plane is provided on itscircumference with a plurality of axially extending circumferentiallyelongated concavities or grooves I90, there being four such groovesprovided as clearly shown in Fig. 8. The grooves I90 extend axially ofthe valve body toward the front of the headstock in the plane indicatedin Fig. '1 and communicate with a circumferential groove I9I formed inthe valve body and always in communication with the passage I18 in thevalve housing or casing andwhich passage, it will be recalled, isconnected to the drain conduit I61.

The passage I82 shown in Figs. 6 and 9 is connected intermediate itsends to a passage I92 formed in the valve casing or housing I16 andextending axially thereof toward the front of the headstock and providedat its forward end with an angled portion communicating with the and I93are out of communication with each other and said passage I92 at suchtimes is deadended by the valve body.

The speed selector or preselector valve S comprises four two-positionvalves. The valve body o casing I94 is provided with a valve chamber I95having longitudinally spaced enlarged portions I96 and I91 which areconnected, respectively, to the conduits HI and I69 that extend to themedium clutch on the shaft 14 and to the high clutch on the shaft 44.Slidable in the valve chamber I 95 is a valve body I98 having annularcutaway portions I99 and 200 with the valve body adjacent such cutawayportions constituting lands. The valve chamber I95 is in communicationintermediate the enlarged portions I96 and I91 thereof with a passage20I formed in the casting or valve body I94 and extending to a valvechamber shortly to be described.

It will be seen that when the valve body'I98 is in the position shown inFig. 11 then conduit I1I is in communication through the valve chamberwith passage 20I and conduit I69 is in communication with a drainconduit I68. It will also be apparent that when the valve body I98 isshifted toward the right to its second operative position that then theconduit I69 will be in communication through the valve chamber with thepassage 20I and conduit IN is in communication with a second drainconduit I68.

The valve body or casting I94 contains a second valve chamber 202extending parallel to the Valve chamber I95 and provided with enlargedportions 263 and 204. The enlarged portion 203 communicates with theconduit I10 that extends to the low clutch on the shaft 14. The enlargedportion 204 of the valve chamber 202 communicates with the passage 20Iwhich, in turn, communicates with the previously described valve chamberI95. A valve body 205 is slidable in the chamber 202 to either one oftwo operative positions and is provided with two cutaway portions 206and 291, with the body adjacent to said portions forming valve lands.The valve chamber 292 on opposite sides of the enlarged portions 203 and294 thereof communicates with the conduit I66 that extends from thespeed selector or preselector valve to the passage I8I in the housingI16 of the main control valve C, i. e., the brake position of the maincontrol valve. The valve chamber 202 intermediate the enlarged portions203 and 204 thereof communicates with the pressure line I51 through thebranch conduit I51c.

It will be seen that when the valve body 265 is in the position shown inFig. 11 that then hydraulic pressure in line I51c is free to flow intothe chamber 202, the enlarged portion 203 thereof and thence through theconduit I10 to the low clutch on the shaft 14. At this time the enlargedportion 204 of the valve chamber 292 is out of communication with thepressure line I510 and communicates. with the passage Bill and with theconduit I66. Also at this time the valve chamber 292 to the left of theenlarged portion 203 is in communication with the conduit I66. When thevalve body 265 is shifted to the right to its second operative positionthen passage 20I communicates through the enlarged portion 294 of thevalve chamber 292 with the pressure line I510 whil the enlarged portion203 of the valve chamber 202. is out of communication with the pressureline I510 and in communication with the conduit I66 and the latter henceis in communication with the conduit I10.

ac'zomca It: will be seen: that the: positions of the valve bodies 198and 205 are interrelated tocontrolthe nigh? clutch on. the shafted and:the: medium arrdf "low clutches on the. shaft I4 and this is for'the'purpose. of obtaining a braking arrangementwhichwilllee-furtherexplained.

Thebody' or casting 5'34 of the speed selector on'preselector valves isfurther provided with a valve chamber 258' similar and parallel to thevalve: chambers I55- and 232 and having spaced enlarged. portions 2539:and E'Iil. The enlarged portl'on; 203* communicates with the conduit iizthat extends to-th'elow"" clutch on the shaft "12. The enlarged portion2 i 9 communicates with the condm't Isl-3" that extends'to the highclutch on the shaft I ilZ. Thevalve-chamber 208 to the left of. theenlarged portion thereof communisates-with drain i53- as does also" thevalve-charm her to the right of the enlarged portion 2 I Hthereofas'viewed in Fig. 11

A valve body 2H is slidable in the chamber 208i to either; one of: twooperative positions and isprov-ided with two cutawayportions 212 and 213with the valve body adjacent said portions constituting lands; in; theoperative position shown in Fig. 11' then the conduit H2? is in.communication with the pressure line IETE through the valve chamberZflland the'eIflargedportion 239 thereof. When the valve. body ZII isshifted to the right to its in;

second operative position then communication between the conduits 4572iand IE2 is closed on" and the conduit 112 is in cornmnnicationv with thedrain conduit I58. At this time the conduit I13 which. communicates withthe enlarged portion' 211% of'the' valve chamber has been disconnectedfrom its communication with drain conduit IE8 and placed incommunication through the valve chamber with pressure line conduitI55'Id1' The casting Hit of the speed selector or preselector valve isprovided with a fourth. valve chamber 214 similar to the valve chamberspreviously described and extending parallel thereto and provided: withlongitudinally spaced enlarged portions 2 I'5-and I26.

The enlarged portion 2 I 5 of the valve chamber 2T4 communicates withconduit I75 that extends to. the "low clutch on the spindle M8. Theenlarged. portion 2 it of the valve chamber 2M communicates with conduitI'M that extends to the high clutch on the shaft 53! The valve chamber2M intermediate the enlarged portions 2I5 and 21:5 thereof communicateswith theconduit IE5 that extends to the passage L52 in the housing I76of the main control valve C and which the neutral position of the maincontrol valve functions as a drain conduit.

The valve chamber 2M to the left of the enlarged portion H5 and to theright of the enlarged portion 2P5 communicates with the drain conduitI68. A valve body 2i? is slidable in the valve chamber 2M and isprovided with longitudinally spaced cutaway portions 2!!) and 2H) withthe valve body adjacent to said cutaway portions forming valve lands. 2His in the first of its two operative positions as indicated in Fig. 11,then conduit I'I5 communicates'with. conduit I65 and when said valvebody ZIT is moved to the right to its second operative position thenconduit I'M communicates with conduit IBS'and is out of communicationwith drain conduit I68 while conduit I75 is in communication with drainconduit I68.

In- OIdEl" t0 shift the valve bodies. 93, 2%, 2H and E'i li to effectengagement of the various When the valve body 2i i is When the valvebody 16 clutches in; the transmission other. than the-forward"andreverse clutches so: as to obta'ur the different selected. orpreselected speeds for. the spindle the fol-lowing mechanism may beemployed: The shaft rel which carries the: hand wheel. orknob: HE? isslidably and rotatably supported intermediate-its ends by a bracket 22!carried by the casting ltd or" the speed selector or" preselecto'r valveand at its inner end said shait- H31 slidably and rotatably interiitsabore 221 formed a portion 222 of the casting. 94". The bore 22I slidablymountsatapered head 223 having a reduced shank or pin portion and saidhead 2E3 engages the-inner end of the shaft iilI. A' coil spring 224surrounds-saidpin or shaft within the bore 2-H and theone end abuts thehead 223 and at the opposite endabuts a threaded plug 225* screwed intotherthreadedend of the bore The spring 22:2 and head 223 act on theshaft it! to" move the same toward its outermost sliding position:andto' maintain theshaft in-such positionzuntil it is moved'inwa-rdly byforce which overcomes the action of the spring 22 2. It willbeundersiood that the lowermost. disk 226 inFig. 11 determinesthe'outward limit of movement of the shaft I61 by its engagement withbracket-22 8 The shaft I8! has fixed thereto four axially spaced.similar disks 225'; The circumferences of the disks 225 are providedwith a plurality of inwardly extending circumferentially spaced recesses223? it being understoz-id that the number, the spacing and the'width ofsaid recesses 2.2T wiii be determined in relation to the' speeds to be"selected. or preselected by the speed selector or presel'ector valve andthat the arrangement and dimensions of the recesses on: the variousdisks 2'23 will vary.

Four rocker members 223 have hub portions 229 which are pivotallysupported on shafts 231] carried, respectively, by four-spa'cedsupporting arms or brackets 2'34 extending fromthe casting i'e i' andione of. which isshown' in Fig. 13.

The rocker members 228 each has spacedparallel arm 5.32 and 233* at theends of which are mounted pins 234 extending'toward the disks 225 andadaptedto project into the recesses 22?- or to'engage the adjacentsurfaces'of'the disks when the shaft I'SI' is moved inwardly against theaction of the spring 224' as clearlyindicated in Figs. 1'1 and 12,wherein it will be noted that a rocking movementis imp-arted to therocker members when oneof'th'e pins'23 t extends into a reo'e ssfiz'iand the other pin 23 engages the ad'- ia'cent surface or the-disk 226*.

Each rocker'228' is provided-with a valvebody actuating arm 23$: whichextends into a' slot 236 in the valve body correlated toparrticular'roeker 223, it being noted that the actuating arms 235adjacent their free ends are provided with roundedsurfaces soa's toimpart-endwise sliding movement to the valvebodies I98; 2&5, 2H and 2-Hwithout lost motion.

A- particular speed for the spindle I46 may be selected or:preselectedvby the operator by turning the hand wheel IE2 and the shaft IfiI whensaidshaftisheldin its outermost position under the action of the spring224,. at which time the disks 22% are spaced from the pins 235 of therockers and are free to rotate. with the shaft without affecting therockers. It will be understood that a suitable: dial is provided wherebythe operator can determine'the: particular position ofrtheshaitanddislcwith-relation to aparticular. speed, wherefore during one operative stepof the machine the operator can preselect the spindle speed for thefollowing operative step.

It will also be understood that suitable means, such as a sprin pointand cooperating recesses or notches will be provided to hold the shaftI6I and disks 226 in their adjusted rotative position. When an operativestep is terminated the operator pushes inwardly on the shaft I6I to movethe disks toward the pins of the rockers, whereupon certain of the pinswill extend into the recesses 221 while other of the pins will engagethe adjacent planular surface of the disks, with the result that certainor all of the rockers will be rocked in a predetermined manner to shiftcertain or all of the valve bodies I98, 205, 2I I and 2I1 to set saidvalve bodies in the proper posi tion to obtain the preselected speed.

Assuming that the lever I69 of the main control valve is in the neutralposition, i. e., the position represented in Figs. 6 to 10' inclusive,it will be seen that at such time the spindle I 46 will be entirelydisconnected from the transmission and will be a free spindle so it canbe freely turned for loading and other purposes.

Referring to Figs. 5 to inclusive, it Will be noted that when the leverI90 is in neutral position the conduits I63 and I64 are disconnectedfrom the pressure side of the hydraulic circuit and are connected todrain conduit I61 through the recesses I99 in the valve body. Hence atsuch time the reverse clutch on the reverse shaft 2| and the forwardclutch on the forward shaft 44 are disengaged and the main drive motorI4 is imparting no power to the transmission. This condition is clearlyillustrated in Figs 6 and 8. Also at this time conduit I65 isdisconnected from the pressure side of the circuit (see Fig. 9) and isconnected through passages I92, I93, annular groove I9! and passage I18with drain conduit I61. Therefore reference to Fig. 11 will show thatconduit I15 which extends to the low clutch on the spindle I46 isconnected to drain through the valve chamber 2M and conduit I65.

In addition, at this time conduit I14 which extends to the high clutchon shaft I30 is connected to drain I68 through valve chamber 2M.Consequently the gear I41 is disconnected from the spindle I46 and thegear I32 is disconnected from the shaft I30 and hence the spindle I46 iscompletely disconnected operatively from the transmission and acondition of free spindle exists.

Furthermore, it will be seen that should the valve body 2 I 1 be in itsother and right hand operative position when the main control valve isin neutral position, that then the conduit I15 is connected through thevalve chamber 2 I4 with drain conduit I66 while the conduit I14 isconnected through the valve chamber with conduit I65 and hence the samecondition obtains irrespective of which operative position the valvebody 2 I 1 mi ht be put in.

When the main control valve is in neutral position and the speedselector or preselector valve of Fig. ll is in the position indicatedtherein, the high clutch controlling the gear 48 on the shaft M isdisengaged since the conduit I69 is connected through the enlargedportion I91 of the valve chamber I95 with drain conduit I68. At thistime, however, the low clutch on shaft It will b engaged since conduitI10 is connected through valve chamber 292 with pressure line I510. Alsoat this time the medium clutch on shaft 1 and controlling gear 11 willbe disengaged since conduit IN is connected through the valve chambersI95 and 292 with conduit I65 that extends to passage It! in the maincontrol valve housing I16 (see Fig. 8.) and said latter passage isconnected through recess I with groove I9I, passage I19 and drainconduit I61. Also at this time low clutch on shaft I92 and whichcontrols gear 99 will be engaged since conduit I12 is connected throughvalve chamber 206 with pressure line conduit II'Id. However, at thistime the high clutch on shaft I02 and which controls gear I05 will bedisengaged since conduit I19 is connected through the valve chamber 2539and particularly enlarged portion 2I0 thereof with the drain conduitI68.

The fact, however, that certain of the speed changing clutches on theshafts 40, 14 and I02 will be engaged in. the neutral position of themain control valve, does not affect the free spindle condition existingsince the high clutch on shaft I99 and the low clutch on spindle I46will always be disengaged at this time.

Assuming that when the main control valve is in neutral position, thevalve body I99 is in the other of its operative positions than thatshown in Fig. 11, then conduits I69 and HI will still be connected todrain and the high clutch on shaft 44 and the medium clutch on shaft 14will be disengaged.

Assuming that valve body 205 is in the other of its operative positionsthan that shown in Fig. 11 when the main control valve is in neutral,then conduit I10 will be connected to drain through conduit I66 and lowclutch on shaft 14 will be disengaged, while medium clutch on shaft 19will be engaged, since conduit I1! will be connected to pressure lineI51. At this time high clutch on shaft 94 is disengaged since conduitI69 is connected to drain.

Assuming that both valve bodies I93 and 205 have been shifted to theirother operative positions than the. one shown in Fig. 11 and the maincontrol valve is in neutral position, then high clutch on shaft 4% willbe engaged asconduit I69 is connected to pressure while the low andmedium clutches on shaft 14 will be disengaged since conduits I10 andIll will be connected to drain.

Assuming that when the main control valve is in neutral position, thatvalve body 2II is shifted to the other of its operative positions thanthat shown in Fig. 11, then conduit I13 will be connected to pressureline I51d and the ,high clutch on shaft I92 will be engaged While thelow clutch on said shaft is disengaged since con duit I12 will now beconnected to drain conduit Assuming. that the lever I 60 of the maincontrol valve is in the forward position and valve body I11 has beenrocked counterclockwise from the position shown in Figs. 6 to 10inclusive, diametral passage I69 of the valve body will register withpassage I90 in the valve housing and hence conduit I64 to the forwardclutch on shaft 44 will now be connected through the valve body topressure line I51a and said clutch will be engaged. At this time passageI19 in the valve housing I16 will still be in communication with arecess I90 and will be connected to the annular groove I9I in the valvebody and through passage I18 with drain conduit I61, and hence conduitI63 will be draining and reverse clutch on shaft 2| will be disengaged.Also at this time passage. I89 in the. valve body I11 will be incommunication with conduit I 65 and hence the latter will be connectedto the pressure side of the circuit and therefore 19 either-the highclutch on shaft I30 or the 10x clutch on the spindle I46 can be engageddepending upon the position of the valve body 2I7 of the speed selectoror preselector valve shown in Fig. 11.

It will be recalled that passage I02 in the housing I75 of the maincontrol valve is now out of registry with passage I93 in the valve bodyI77 and hence said passage I92 is not connected to drain. Also at thistime conduit I66 will be connected to drain through a recess I 90 in thevalve body I77 and hence pressure from the line I570 can be suppliedselectively to conduits I70, I7! and IE9, depending upon the adjustedposition of valve bodies 205 and I08 of the speed selector orpreselector valve. This is also true with respect to conduits I72 andI73 which selectively can receive pressure from the line I57d, dependingupon the adjusted position of the valve body 2! I.

It will thus be seen that when the forward clutch is engaged the reverseclutch will be disengaged while the engagement or disengagement of theother clutches in the transmission will be effected through the settingand actuationof the speed selector or preselector valve to produce thedesired speed for a particular operative step. The same situationobtains when the main control valve is in reverse position, that is,when it has been rotated in a clockwise direction as viewed in Fig. 8 tobring the diametral passage I89 into communication with the passage I79and the conduit IE3 to subject the reverse clutch to the pressure sideof the circuit. At this time the forward clutch. will be drainingthrough a recess I90 in th valve body as will also conduit I66.Furthermore, at this time conduit I65 will be in communication throughan enlarged end I88 with the passage I87 in the main control valve bodyI 77 and hence will be subject to hydraulic pressure.

When the main control valv is moved by the lever I60 to brake" position.th valve body I77 will be rotated in a clockwise direction from theposition shown in Figs. 6 to 10 inclusive to place the conduit I 65 incommunication through an enlarged end I88 with the diametral passage I87in the valve body and hence in communication with the pressure side ofthe circuit. Therefore, either the low clutch on the spindle I46 or thehigh clutch on the shaft I30 will be engaged,

depending upon the position of th valve body 2 I7 of the speed selectoror preselector valve. Hence the spindle I 46 will be operativelyconnected through the shaft I30 and gears I28 and I27 with the shaftI02. At this time either the low or the high clutch on shaft I02 will beengaged, depending upon the position of valve body 2 II of the speedselector or preselector valve and hence the spindle will be operativelyonnected with shaft 74, since shaft I 02 will be connected to shaft 74either through gears 99, 97 or I05, 98. At the time under discussion theclockwise rotation of valve body IT! or the main control valve will haveplaced conduit I65 in communication with diametral passage I89 and hencewith the pressure side of the circuit. Therefore if valve bodies 205 andI98 of the speed selector or preselector valve are in the position shownin Fig. 11 conduit I70 will be connected to pressure conduit I57 and thelow clutch on shaft 74 will be engaged. Also conduit I66 which is now apressure conduit will be connected through valve chamber 202, passage20I with valve chamber I95 and thence with conduit ITI, wherefore the"medium clutch on shaft 4 wi l also be engaged.

Supposing that valve body 205 of the speed selector or preselector valveis shifted to its other operative position than shown in Fig. 11, whilebody I98 remains in its illustrated position, then conduit I will beconnected to conduit I 66 which is now a pressure conduit and the lowclutch on shaft 74 will. be engaged. Also at this time pressure line I57will be connected through valve chamber 202 and passage 20I with valvechamber I05 and with conduit I7I, wherefore the medium clutch on shaft74 is engaged. In other words, shifting of valve body 205 from theposition shown in Fig. 11 to its other operative position when the maincontrol valve is in brake position will not alter the situation ofhaving both the low and medium clutches on shaft 74 simultaneouslyengaged' Now supposing that valve body I98 is shifted to its otheroperative position from that shown in Fig. 11 when the main controlvalve is in brake position but that valve body 205 remains in itsillustrated position, then the low clutch on shaft 74 is engaged whilethe high clutch on shaft 44 is engaged and the medium clutch on shaft 74is disengaged. Now further assuming that both valve bodies I98 and 205have been shifted to their other operative positions than the onesillustrated in Fig. 11 when the main control valve is in brake position,then the low clutch on shaft 74 will be engaged as will also the highclutch on shaft 04, while the medium clutch on shaft 75 will bedisengaged. It will be seen consequently that irrespective of theoperative positions of the valve bodies I98 and 205 the low clutch onshaft 74 will be engaged when the main control valve is in the brake"position and also that the medium" clutch on shaft 74 of the high clutchon shaft 44 will be simultaneously engaged. Consequently two separategear trains of different size will be simultaneously engaged and willact in opposition to each other to prevent or brake rotation of theshafts 74, I02, I30 and the spindle I46. This braking arrangement can besafely utilized inasmuch as all of the clutches are friction clutchesand any overloadin of the parts will merely produce slippage in theclutches and will not damage the parts, it being understood that thehydraulic pressure acting on the simultaneously engaged clutches will beof predetermined amount so as to allow this necessary slippage.

It will have been seen that the speed changes can be effected withoutthe necessity of disconnecting the input shaft from the transmissionsince the clutches are friction clutches and can be engaged anddisengaged with the power applied to the transmission and since thereare no gears to shift the change from one speed to another will beeffected silently.

It will also be understood that when the machine is operating at onespeed in an operative step of the work cycle the operator can preselectthe spindle speed for the next operative step merely by indexiblyturning the hand wheel I62 of the speed selector or preselector valve tothe desired speed position. Then upon completion of the one operativestep, assuming there is to be no change in the direction of rotation ofthe spindle, the operator obtains the preselected speed for thesucceeding operative step merely by moving the hand wheel I62 and theshaft IIiI axially inwardly to cause .the disks 226 to rock the rockers228 in a predetermined manner to shift one or more of the sliding valvescontained in the speed selector or preselector valve. This 21 inwardmovement of the shaft l6! and wheel I62 sets up the hydraulic circuit toengage or disengage in a predetermined way the various clutches toobtain the preselected speed. The operator after pushing the hand wheelI62 and the shaft I6! inwardly to obtain the preselected speed merelyreleases the hand wheel whereupon the spring pressed plunger 223restores the shaft [6| to its outwardly moved position wherein it can berotatably indexed again to preselect the spindle speed for the nextoperative step in the work cycle. Of course if the spindle has beenrotating in one direction during one operative step and it is desired tohave it rotate in the opposite direction during the next operative stepthe operator, in addition to moving the hand wheel E62 and shaft I6!inwardly to obtain the preselected spindle speed, must also move thecontrol lever of the main control valve from forward position to reverseposition or vice versa as the case might be.

From the foregoing detailed description it will be apparent that theobjects and advantages of the invention hereinbefore enumerated areadequately obtained by a construction embodying the invention.

Although a preferred embodiment of the invention has been illustratedand described herein, it will be understood that the invention issusceptible of various changes and modifications thereover and whichcome within the scope of the appended claims.

Having thus described our invention, we claim:

1. In a change speed transmission adapted to be used in a machine toolheadstock having a power input shaft and a rotatable driven member suchas a spindle, a rotatable shaft par allel to said input shaft and drivenmember and having gears fixed thereto adjacent its opposite ends and apair of gears freely rotatable there on intermediate said fixedgearswith one of said freely rotatable gears operatively connected withsaid input shaft, separate clutch means on said rotatable shaftengageable to interconnect said freely rotatable gears therewith, anintermediate shaft parallel to said input shaft and said rotatable shaftand provided with gears freely rotatable thereon and constantly meshingwith said fixed gears o-rrsaid rotatable shaft, separate clutch meansengageable to interconnect said last mentioned freely rotatable gearswith said intermediate shaft, a gear on said intermediate shaftintermediate the freely rotatable gears thereon and meshing with theother freely rotatable gear on said rotatable shaft, end gears fixed tosaid intermediate shaft and located thereon outwardly of said freelyrotatable gears on said intermediate shaft, and gear means operativelyinterconnecting said fixed gears on said intermediate shaft with saiddriven member. I

2. In a change speed transmission as defined in claim 1 and wherein theclutch means for interconnecting said other freely rotatable gear onsaid rotatable shaft with said shaft and the separate clutch means forinterconnecting the freely 1 rotatable gears on said intermediate shaftwith said shaft are friction clutches.

3. In a change speed transmission as defined in claim 1 and wherein theclutch means on said rotatable shaft and said intermediate shaft arefriction clutches and power means is provided for engaging said frictionclutches. *1:

4.. In a change speed transmission as definedin claim 3 and wherein saidpower means includes a control device indexible during a current oper-22 ation of the transmission-to-prese1ect the clutch means to be engagedin the following operation of the-transmission and movable endwise atthe end of said current operation of the transmission to obtain thepreselected clutch means engagement.

5. Ina change speed transmission as defined in claim 3 and wherein saidpower means is hydraulic means and includes a hydraulic circuit havingtherein a control valve indexible to preselect during a currentoperation of the transmission the clutch means engagement .for thefollowing operation thereof and movable at the end of said currentoperation of the transmission to obtain the preselected clutch meansengagement for the following operation of the transmission.

6. In a change speed transmission as defined in claim 5 and wherein saidcontrol valve includes a plurality of shiftable valve bodies, individualrocker members for shifting said bodies and individual elements normallyout'of contactwith said rocker members and indexible to preselect clutchmeans engagement and movable axially into contact with said rocker meansto rock the same and shift said valve bodies to obtain the preselectedclutch means engagement.v

'7. In a change speed transmission adapted to be used in a machine toolheadstock having a power input shaft and a rotatable driven member suchas a spindle, a reverse shaft having a gear freely rotatable thereon andoperatively connected with said input shaft, clutch means on saidreverse shaft engageable to interconnect said freely rotatable geartherewith, and a gear fixed to said reverse shaft, a forward shafthaving a pair of gears freely rotatable. thereon .and one of which isoperativelyconnected with said input shaft, separate clutch means onsaid forward shaft engageable to interconnect said freely rotatablegears thereon with said forward shaft, an end gear fixed to said forwardshaft and located outwardly of said one freely rotatable gear, a secondgear fixed on said forward shaft and located outwardly of the other ofsaid freely rotatable gears thereon and meshing with the gear fixed onsaid reverse shaft, an end gear fixed on said forward shaft outwardly ofsaid second gear fixed thereon, an intermediate shaft parallel to saidpreviously mentioned shafts and having fixed thereto a gear meshing withthe other of the freely rotatable gears on said forward shaft, freelyrotatable gears on said intermediate shaft on the opposite sides of saidfixed gear thereon and meshingwith the fixed end gears on said forwardshaft, clutch means engageable to interconnect said freely rotatablegears with said intermediate shaft, end gears fixed to said intermediateshaft adjacent the ends thereof and outwardly of said freely rotatablegears thereon, and gear means interconnecting said end gears on saidintermediate shaft with said driven member.

8. In a change speed transmission as defined in claim '7 and whereinsaid clutch means are friction clutches, and hydraulic power means isprovided for actuating said clutches and including a control deviceindexible to preselect during a current operation of the transmissionengagement of certain of said clutches for the following operation ofthe transmission and movable at the end of of said current operation ofthe transmission to obtain the preselected clutch means engagement.

9. In a change speed transmission as defined in claim '7 and wherein thegear ratios of the other freely rotatable gear on the forward shaft andits intermeshing fixed gear on the intermediate shaft is different fromthe gear ratios of the freely rotatable gears on the intermediate shaftand their intermeshing fixed gears on the forward shaft, while powermeans is provided for actuating said clutch means and including a powercircuit having therein a control device such that any two of the twoclutch means on the intermediate shaft and the clutch means for theother freely rotatable gear on the forward shaft can be simultaneouslyengaged to produce a braking action to the rotation of said shafts andsaid driven member because of the different gear ratios of the opposinggear trains.

10. In a change speed transmission as defined in claim 7 and wherein thegear means interconnecting the end gears on the intermediate shaft withthe driven member includes a second intermediate shaft having thereon apair of freely rotatable gears meshing with the fixed end gears on saidintermediate shaft, clutch means on said second intermediate shaftengageable to interconnect said freely rotatable gears thereon with saidsecond intermediate shaft and an end gear fixed on said secondintermediate shaft outwardly of one of said freely rotatable gearsthereon.

11. In a change speed transmission as defined in claim 10 and whereinsaid gear means which interconnects said end gears on said intermediateshaft with said driven member further includes a third intermediateshaft having thereon fixed gears one of which constantly meshes with thefixed end gear on the second intermediate shaft, a freely rotatable.gear on said third intermediate shaft intermediate the fixed gearsthereon, and clutch means on said third intermediate shaft engageable tointerconnect said freely rotatable gear with said shaft; and a fixedgear on said driven member intermeshing with the freely rotatable gearon said third intermediate shaft, a freely rotatable gear .on saiddriven member intermeshing with the other fixed gear on said thirdintermediate shaft, and clutch means on said driven member engageable tointerconnect said freely rotatable gear therewith.

12. In a change speed transmission adapted to be used in a machine toolheadstock having a power input shaft and a rotatable driven member suchas a spindle; a reverse shaft having a gear freely rotatable thereon andoperatively connected with said input shaft, clutch means on saidreverse shaft engageable to interconnect said freely rotatable gear withsaid reverse shaft, and a gear fixed to said reverse shaft; a forwardshaft having a pair of gears freely rotatable thereon and one of whichgears is operatively connected with said input shaft, separate clutchmeans on said forward shaft engageable to interconnect said freelyrotatable gears thereon with said forward shaft, a gear fixed on saidforward shaft and meshing with said gear fixed on said reverse shaft,and end gears fixed to said forward shaft adjacent the opposide endsthereof; an intermediate shaft having freely rotatable thereon a pair ofgears constantly meshing with the end gears fixed to said forward shaft,said freely rotatable gears on the intermediate shaft being of adifferent size than the corresponding intermeshing gears on the forwardshaft, a gear fixed to said intermediate shaft intermediate the freelyrotatable gears thereon and meshing with and of a 24, different sizethan the other freely rotatable gear on said forward shaft, separateclutch means on said intermediate shaft engageable to interconnect saidfreely rotatable gears with said intermediate shaft, and end gears fixedon said intermediate shaft adjacent the opposite ends thereof; a secondintermediate shaft provided with a pair of freely rotatable gearsthereon meshing with and of a different size than said end gears on saidintermediate shaft, separate clutch means on said second intermediateshaft engageable to interconnect said freely rotatable gears thereonwith said second intermediate shaft, and an end gear fixed on saidsecond intermediate shaft adjacent an end thereof; a third intermediateshaft having thereon end gears fixed thereto adjacent its opposite endsand one of which end gears meshes with and being of a different sizethan the end gear fixed on said second intermediate shaft, a gear freelyrotatable on said third intermediate shaft, clutch means on said thirdintermediate shaft engageable to interconnect said freely rotatable gearwith said third intermediate shaft; a gear fixed on said driven memberand meshing with the freely rotatable gear on said third intermediateshaft, a gear freely rotatable on said driven member and meshing withthe other end gear fixed to said third intermediate shaft, and clutchmeans on said driven member engageable to interconnect said freelyrotatable gear with said driven member.

13. In a change speed transmission as defined in claim 12 and whereinsaid clutch means are friction clutches and power actuators are providedfor actuating the same.

14. In a change speed transmission as defined in claim 12 and whereinsaid clutch means are friction clutches and hydraulic means are providedfor actuating said clutch means and including a hydraulic circuit havingtherein a main control valve controlling the clutch means on saidreverse shaft and the clutch means on said forward shaft whichinterconnects said one free- 1y rotatable gear therewith, and alsohaving therein a speed selector valve means which is indexible during acurrent operation of the transmission to preselect the speed of thedriven member during the following operation of the transmission and ismovable at the end of said current operating of the transmission toobtain the preselected speed by engaging certain other of the clutchmeans on said shafts.

15. In a change speed transmission adapted to be used in a machine toolheadstock having a power input shaft and a rotatable driven member suchas a spindle, an intermediate shaft parallel to said input shaft andspindle and having gears fixed thereto adjacent its opposite ends and apair of gears freely rotatable thereon intermediate said fixed gears,operative connections between said freely rotatable gears and said inputshaft and including means for rotating said free- 1y rotatable gearsselectively in opposite directions, separate clutch means on saidintermediate shaft selectively engageable to interconnect therewith thesaid freely rotatable gears threon, a second intermediate shaft parallelto the previously named shafts and having thereon freely rotatable gearsconstantly meshing with the gears fixed on said first named intermediateshaft, separate clutch means on said second intermediate shaftselectively engageable to interconnect therewith the said freelyrotatable gears thereon, and gear means operatively interconnecting saidsecond intermediate shaft with said driven shaft and including a gearfixed on said second intermediate shaft adjacent an end thereof andoutwardly of one of the freely rotatable gears thereon, a shaft parallelto said second intermediate shaft and to said driven member and having agear freely rotatable thereon and a gear fixed thereto, a clutch on saidlast mentioned shaft for operatively connecting therewith said freelyrotatable gear thereon, a gear fixed on said driven member andintermeshing with said last mentioned freely rotatable gear, a gearfreely rotatable on said driven member and meshing with the gear fixedon said last mentioned shaft, and clutch means on said driven member foroperatively connecting therewith the freely rotatable gear thereon.

16. In a change speed transmission as defined in claim 15 and whereinthe clutch means on said intermediate shafts are friction clutches andpower means is provided for engaging said friction clutches.

17. In a change speed transmission as defined in claim 16 and whereinsaid power means includes a control device indexible during a currentoperation of the transmission to preselect the clutch means to beengaged in the following operation of the transmission and movableendwise at the end of said current operation of the 26 transmission toobtain the preselected clutch means engagement.

18. In a change speed transmission as defined in claim 16 and whereinsaid power means is hydraulic means and includes a hydraulic circuithaving therein a control valve indexible to preselect during a currentoperation of the transmission the clutch means engagement for thefollowing operation of the transmission and movable at the end of saidcurrent operation of the transmission to obtain the preselected clutchmeans engagement for the following operation of the transmission.

HARRY SCHOEPE. HENRY W. SPREITZER.

References Cited in the file of this patent UNITED STATES PATENTS NumberName Date 832,381 Hartness Oct. 2, 1906 847,572 Hanson Mar. 19, 19071,342,126 Macnab et a1 June 1, 1920 1,605,931 Emmes Nov. 9, 19261,987,006 Foster Jan. 8, 1935 2,050,520 Carter Aug. 11, 1936 2,156,596Lloyd May 2, 1939 2,227,620 Armitage et al Jan. 7, 1941 2,357,427 RuppelSept. 5, 1944 2,594,782 Makant et a1. Apr. 29, 1952

